Combined typewriting and computing



May 31, 1938.

H. L. PITMAN COMBINED TYPEWRITING AND COMPUTING MACHINE 3 Sheets-Sheet 1 Filed Dec. 13, 1932 FIG.\

INVENTOR: W

ATTORN y 31, 1933- H. L. PlTMAN 2,118,861

COMBINED TYPEWRITING AND COMPUTING MACHINE Filed Dec. 13, 1932 3 Sheets-Sheet 2 Ii INVENTOR- BY W ATTO EY.

ya-1 1938. H. L. PITMAN 2,118,861

COMBINED TYPEWRITING' AND COMPUTING MACHINE Filed Dec. 15, 1932 3 Sheets-Sheet 5 ElIIEl3|ElEllEIIEIHIEIIIIEIEIEIEIIBIL FIGJZ.

K II/ A Illi- ATTO EY.

Patented May 31, 1938 UNITED STATES PATENT OFFICE COMBINED TYPEWRITING AND CODIPUTING MACHINE Delaware Application December 13, 1932, Serial No. 646,953

30 Claims.

This invention relates to combined typewriting and computing machines wherein numeral-type keys operate individual digit-entering trains to drive a master-wheel which may be normally disconnected from the drive trains, and with which denominational gear-trains of a totalizer are engaged seriatim as the totalizer travels with the carriage through a computing zone.

The invention provides novel features of improvement over the full-stroke device, the masterwheel-clutch-actuating device, and other related devices, shown in the co-pending application of Otto Thieme, filed July 15, 1930, Serial No. 468,175, Patent No. 2,020,340, dated November 12, 1935.

It is contrived to make the displacement of any full-stroke pawl, between opposite trailing positions, operate the master-wheel-clutch-actuating mechanism and to also operate totalizer-controls, such as totalizer-gear aligners and totalizer-carrying-wheel controls. These operations, through the agency of the full-stroke-pawl movements, may be effected, as will be shown, by simple trains of connections, and the number and nature of the parts as compared with the parts heretofore used are greatly reduced and simplified. This conduces to economy in manufacture and maintenance and also to reliability in the functioning of the machine.

Each actuator-train is provided with. an individual full-stroke dog or pawl. A universal member co-operates with the series of full-stroke dogpawls in such a way that the displacement of the full-stroke pawl to trailing position when an actuator is operated in a computing stroke causes said universal member to be operated. At the end of said computing stroke, the pawl escapes from the actuator-train in the usual manner so that it may be reversed, such escape permitting the universal member to return to a normal position. Each full-stroke pawl is so related to the universal member that although the pawl is effective to displace said universal member from its normal position in the computing stroke of the actuator-train, the reverse displacement of the pawl, which takes place in the return stroke of the actuator-train, is ineffective to move said universal member beyond its stopping point.

The movement of the universal member thus shifting from a normal position at the beginning of the key-stroke and back to normal position at the end of the key-stroke may be utilized to actuate the master-wheel-clutch-actuating mechanism and certain totalizer-controls which need to be actuated at each denomination,

In the. reverse stroke of the actuator-train the full-stroke pawl may, by reason of its reverse po sition, cause the universal member to be locked in the normal position to which it is returned, the pawls being further related to the universal member in such a way that the universal member so locked holds the inactive pawls against displace.- ment by their respective actuators until the active actuator-train has completed its return stroke. It results therefore that at no time during the reverse stroke of an actuator-train, and not until such reverse stroke has been completed, can any other actuator-train be operated because the pawl of such other train cannot receive its usual displacement since it is locked by the locked universal member. The parts may be arranged so that only upon full completion of the reverse stroke of an actuator can its trailing pawl escape and return to normal position, thus freeing the universal member so that any other actuator or the same actuator that was just operated may be actuated in a normal down stroke.

In the preferred form of practicing the invention, the series of full-stroke pawls co-operate with swingable actuators, each having a partly toothed periphery with which the respective pawl co-operates.

The series of pawls is mounted along and pivoted on a rock-shaft which constitutes the universal member, the shaft extending crosswise. of the actuators. Each pawl is pivoted on said shaft so that it may have a limited swing relatively to the shaft as determined by a suitable stop-device. On the down or computing stroke of an actuator, the pawl is given a downward swing as it is displaced by a lower corner of the actuator-sector, said corner forming a lower end of the toothed edge with which the pawl coacts. By reason of its stop-device connection with the universal shaft, the pawl in such downward swing rotates the shaft to an angular position in which the shaft, together with the pawl, remains throughout the time that the pawl trails said periphery.

As soon as a corner forming an upper end of said sector-edge passes the tip of the pawl, a spring applied to the universal shaft is enabled to rotate the shaft and return the same to a normal position against a stop; and the shaft, thus returning, carries the pawl with it. The return stroke of the actuator then causes the pawl to trail the actuator-periphery reversely. This reverse displacement of the pawl on the shaft takes up all the extent of relative displacement between the pawl and shaft permitted by the stop-device, and the shaft is thus held in its normal position against contrary rotation, the pawl reacting against the sector which it trails reversely. With the shaft thus held no other actuator can be operated during the return stroke of the actuator since the pawl for said other actuator cannot be displaced.

The full-stroke shaft or universal member and a master-wheel-clutch-operating lever are relatively disposed so that the rocking of said shaft from and back to normal position directly actuates said lever to clutch and unclutch the master- Wheel at each key-stroke, the lever and shaft being provided with co-operating lever-actuating devices.

The clutch-lever may also have formed thereon a totalizer-gear-aligning blade which when the lever has been moved to unclutch the masterwheel serves to align and also to lock the denominational gear-trains of the totalizer. As set forth in said Thieme application, said aligning blade may be limited in length and may be disposed endwise of an auxiliary aligning blade. The latter blade may also be operated by the full-stroke universal shaft. By means of said blades spirality of the transverse lines of totalizer-gears, caused by the cumulative backlash in successive totalizer-trains and carry-over coupling devices, is eificiently corrected.

A master-dog of the actuator-mechanism, which needs to be actuated at every key-stroke for displacing certain carry-over devices seriatim, is also operated by the rocking of the full-stroke universal shaft. Means for locking the totalizertruck and for effecting timed locking and unlocking of the master-wheel at each key-stroke may also be actuated by means of the full-stroke universal member.

Other features and advantages will hereinafter appear.

In the accompanying drawings,

Figure 1 is a perspective view showing a totalizer and a portion of the actuator-mechanism, and also showing the novel full-stroke pawls and the novel means whereby said pawls co-operate with the master-wheel clutch and with other devices.

Figure 2 is a front-elevation view of a series of totalizer-gears, showing how said gears are aligned by means of the full-stroke-pawl universal shaft.

Figure 3 is a perspective view showing details of a totaliZer-gear-aligning part, a driving arm therefor, and an adjacent part.

Figure 4 is a side view of a section of the totalizer and actuator mechanism showing how the universal shaft is arranged relatively to a master-wheel-clutch lever and to the parts seen in Figure 3, all the parts being shown in their normal positions.

Figure 5 is a side elevation of the totalizergear-aligning part and driving arm seen in Figure 3.

Figure 6 is a side View showing, in section, part of the typewriter, a totalizer, and the key-controlled-totalizer-actuator mechanism.

Figure '7 is a perspective View showing how the full-stroke pawls and universal shaft co-operate with an actuator, moving in a return stroke, to lock another actuator against operation during said return stroke.

Figure 8 is a side-view section of the totalizer and actuator mechanism showing how, during the first part of the actuator down stroke, the parts are actuated in correlation to the partial shift of the master-wheel-clutch lever which precedes the withdrawal of a holding tooth from the master-wheel.

Figure 9 is a front-elevation view showing the positions of the clutch-lever and other parts which result from the operation indicated in Figure 8.

Figure 10 is a front view showing the partial shift of master-wheel-clutch element which results from the operation indicated in Figure 8.

Figure 11 is a side-view section of the totalizer and actuator mechanism showing the actuator at a point in its down stroke following the Figure 8 position, the universal shaft having now been fully rocked to operate the parts for completing the shift of the master-wheel clutch and completing the unlocking of the totalizer-gears.

Figure 12 is a view showing, in front elevation, the parts in the positions corresponding to Figure 11.

Figure 13 is a front elevation of the totalizergears and indicates the spirality which is liable to exist in the totalizer-gears when the actuator has completed its down stroke.

Figure 14 is a side-view section of the totalizer, and actuator mechanism, showing the actuator at a point in its return stroke, where the fullstroke pawl, which has escaped at the end of the down stroke, is engaged and is about to be rotated reversely by the actuator to aid the reverse rotation of the universal shaft.

Figure 15 is a view showing, in front elevation, the parts in the positions corresponding to Figure 14.

The Underwood typewriter partly shown in Figure 6 includes a frame Zil having front and rear rails 28, 22, on which there travels a car riage 23 carrying a platen 24. Numeral-typekey levers 25 swing about a fulcrum 25 in said frame and by means of bell-cranks 2i swing type-bars 28 about the usual arcuate fulcrumrod 29. The Underwood carriage-escapement and letter-feeding mechanism is indicated at 3B.

The computing mechanism includes a totalizer 3! which travels with the typewriter-carriage 23 and is therefore mounted upon a plate 32 combined with a rail 33 to form a totalizer-truck, said truck being connected to the carriage 23 by means of arms 34. Anti-friction rolls 35 enable the totalizer-truck rail 33 to ride along a rail 36 formed on a frame 3'! which houses the totalizer-actuator mechanism driven by the numeral-type keys 25. Said actuator-frame 3! extends across the front of the typewriter-frame 28 and is secured thereto by screws 38. Each keylever 25 has a spring 38 forcing the key-lever to return its type-bar train after the printing stroke, each key-lever having a stop-ear 4G normally abutting a cross-bar 4!, supported by the typewriter-frame.

Upon a fulcrum-rod 42 a series of digit-enter ing actuators 43 is swingably supported. A. link 43 connects each key-lever 25 with a corresponding actuator 43. Each actuator has a spring 44 urging the actuator to rotate clockwise of Figure 1, so that a nose 45 of said actuator normally abuts a face of the actuator-frame 3?. A series of arms 46, one for each actuator, is fastened to a rock-shaft 47, each arm carrying a roll 48 which fits a cam-slot 49 of the actuator, the roll 48 being normally clear of the slot, as in Figures 1 and 6.

Upon depression of any numeral-key lever 25, the corresponding actuator is swung downwardly about the fulcrum-rod 42, and the rock-shaft 41' is thereby rotated to a degree depending on the throw of the cam-slot 49, said throw being proportionate to the digit-value of the numeralkey lever.

The differentially rockable shaft 41 worked by the digit-entering actuators 43, has also fastened thereto an arm 58, connected by a link to a gear-sector 52 forming part of a computing wheel driving train. Said gear-sector is, by adding and subtraction setting means, not shown, described in Thieme Patent 1,971,544, dated August 28, 1934, shiftable sidewise together with said link 5|. To accommodate the sidewise shift of the link 5|, a pivot-stud 5W, whereby said link is connected to the arm 58, is made elongate, as seen in Figure 1. The gear-sector 52 swings about a fulcrum 52 The facewise shift of the gear-sector 52 is ac companied by an opposite shift of a computing pinion reversing idler 53 which is rotatable on a stud 54 projecting from. a plate 55 extending forwardly from the actuator-frame 31 (see Figure 1). Spaced from said plate 55 is a similar plate 56, the two plates supporting therebetween certain other parts of the actuator-mechanism. The actuator-fulcrum rod 42 and the differentially rockable shaft 41 are journaled in end plates 51 of the actuator-frame.

In the normal state of the actuator-mechanism, the gear-sector 52 meshes with. a pinion 58, of said computing wheel driving train, rotatable upon a shaft 59, supported between the inner plates 55, 56. Said pinion 58 is retained against sidewise displacement in either direction by suitable means, including a collar 68 (Figure 1). The computing pinion reversing idler 53 may also mesh with the pinion 58, but, normally, does not mesh with the gear-sector 52. The pinion 58, therefore, would be rotated clockwise of Figure 1 for addition, upon a downward stroke of the gearsector 52.

For reversing the rotation of the pinion 58 for subtraction, the sector 52 is shifted leftward out of mesh from the pinion 58. In order to avoid losing the relative angular positions of the gearsector 52 and pinion 59, the idler 53 is shifted sidewise toward the sector 52 at the same time the latter is shifted. The teeth of the sector thereby engage the idler before said teeth leave the pinion 59, said idler never being unmeshed from the pinion 58.

Mounted for rotation on the same shaft 59 with the pinion 58, is a master-wheel 63 having a slotted flange 54 which slidably fits tongues 65 formed at one end of a clutch-element 66, the latter being slidable along the shaft 59 and having at its other end teeth 61 which may engage slots 68 formed around a flange 69, spaced rightward from the pinion 58 by a sleeve 18 and formed integral with said pinion. Normally the clutch-element is positioned to the right as seen in Figure 1, its teeth 61 being then disconnected from the flange-slots 68 of the pinion 58. The tongues 65 are of such length that the clutchelement is permanently connected to the masterwheel 83. Said master-wheel is retained against lateral displacement on the shaft 59.

The totalizer 3| includes a series of denominational gear-trains, each having a gear 15, which, through an idler 16, drives a dial-pinion 11. Upon a shaft 19, supported in a totalizer-casing 88, the several dial-pinions 11 are individually rotatable. Similar shafts 82 and 83 respectively support the idlers 1B and gears 15. During the travel of the totalizer with the typewriter-carriage 23 through a computing zone, the totalizergears 15 are engaged seriatim in denominational order by the master-wheel 63.

Each totalizer-gear 15, except the one of highest denomination, is provided with carry-over teeth 85. Carry-over coupling between a gear 15 and a similar gear of next higher denomination is effected by a Geneva-wheel-and-pinion device, generally indicated by the reference number 85 and operative substantially as set forth in Patent No. 1,876,696, to A. G. F. Kurowski, dated September 13, 1932. Each Geneva-wheel-andpinion device is pivoted at 88 on a lever 89, the several levers being individually swingable on a fulcrum-rod 99. Preparatory to rotation of a totalizer-train by the master-wheel 93, the Geneva-wheel-and-pinion device 86 connecting said train to the trains of lower denomination is lifted (see Figure 8), in order that said rotation may not affect, or be impeded by, said lower denominatiomtrains. Said levers 89 are therefore operated seriatim, as will be explained, in suitably timed relation with the seriatim operation of the totalizer-gear trains by the masterwheel.

Simultaneous operation of more than one keylever is prevented by means set forth in the application of Thieme, 286,218, filed June 18, 1928 (now Patent No. 1,971,544, dated August 28, 1934). Said means include a series of roundended rods 93 confined end to end within a longitudinal slot of the cross-bar 4| and with only enough end play to admit only one link 43- at a time. Each link 43 has a beveled lip 94, whereby, in its descent, it may be entered between adjoining rods 93 to fully take up said end play, and thereby lock other keys against operation. A plate 95, resting upon the cross-bar 4|, retains the locking rods and may be perforated to guide the links 43 each of the latter being articulated to its key-lever 25 by a pin-and-slot connection 91.

99 is a transverse channel-bar supported at the front of the actuator-mechanism and serving to support the totalizer 3!, which is accordingly provided with a co-operating antifriction roll I88.

As will now be described, the master-wheelclutch element 96, the carry-over levers 89 and other totalizer-controls are operated by novel and simple trains called into action by operation of any key-lever 25 and its actuator 43. It is a feature of the invention that said trains may be operated through the agency of a. novel full-stroke mechanism associated with the series of actuators 43.

A universal member, whereby the full-stroke mechanism operates said last-mentioned trains, is preferably in the form of a rock-shaft I8I, also referred to as a cycling element, fitting between the end plates 51 of the actuator-frame and being journaled therein by means of pivotscrews 5B2. Spaced along said rock-shaft I8I is a series of full-stroke dogs or pawls I03, one for each actuator. Each. pawl has a finger I84, whereby it may trail an edge I95 of the actuator 43, said edge terminating at a lower corner I86 and at an upper corner I81 of the actuator. Each pawl I83 has a pair of spaced, perforated ears ")8, whereby it is pivoted upon the rockshaft to swing relatively to the latter. For limiting said swing, for reasons which will appear, a portion I99 of the pawl, from which the ears I88 are bent, has a perforation III) in which plays a pin III, projecting from the shaft I8I. The perforation IIO may fit the pin sidewise, so as to retain the pawl lengthwise of the shaft lol.

It will be seen that the extent of the pawlswing relative to the shaft IGI is limited by the length of the perforation IIil. Normally, that end of said perforation which is farthest from the pawl-finger Hi l is kept in abutment with the pin III by a torsion spring IE2 disposed between the ears I38. Said spring may react on a lower part of the pin III, which accordingly extends through the shaft IllI.

An arm H3, fastened to the rock-shaft IOI, has a roll II4 co-operating with a cam-slot H5 formed at the end of an arm IE3 of a lever Ill, pivoted on a stud IE8, projecting from the plate 56 of the actuator-frame. Another arm of said lever II 1 includes the pivot-hole and is in the form of a block IE3, upon which teeth I23 may be formed. The cam-slot arm II3 is secured to the block M3 by rivets I2I. Extending along the totalizer-truck 32 is a rack I22, with which the teeth I26 may interlock to hold said truck when the lever I I7 is swung about its pivot from a normal position, said teeth clearing said rack in said normal position, as indicated in Figures 1 and 4. A spring E24 urges the universal shaft Eel to rotate counterclockwise of Figure 4. Such rotation is limited by abutment of the roll H4 with the end of the cam-slot H5, and, as seen in Figure 4, the normal positions of said rockshaft I and of the lever II] are thereby established.

With the pawl universal shaft IliI in normal position and the end of the pawl-perforation HG abutting the pin I l I, as stated, the free ends of the pawl-fingers I4 are in neutral positions in which they underlie the lower corners I595 of the actuators when the latter are in their normal positions, as in Figure 1. A downward stroke of any actuator 43 will therefore displace the corresponding pawl to a position in which the pawl-finger trails the actuator-edge I95, as seen in Figure 11. By reason of the pin-and-slot connections of the pawls 33 to the universal rockshaft Hill, the latter is rocked against the tension of its spring I 24 concurrently with the downward displacement of the pawl.

Referring to Figures 1 and 11, it will be seen that the actuator down stroke can have no effect upon the master-wheel-actuating rock-shaft 47 until a camming portion I25 of the actuatorcam slot 49 engages the roll 48 of the operating arm 43 for said latter rock-shaft, a dwell I2? of the actuator-cam slot leading to said camming portion. Thus, during the initial portion of the actuator down stroke, there is afforded time for shifting the master-wheel-clutch element 66 leftward of Figure 1. The master-wheel 63 is therefore connected with the pinion 58 before the latter is rotated by means of the previouslydescribed train, which, it Will be remembered, includes the rock-shaft 41, the arm 53, the link 5I and gear-sector 52.

The described rocking of the universal shaft mi from the position seen in Figures 1 and 4 to the Figure 11 position is utilized to shift the clutch-element 66. Across the front of the actuator-frame 31, there extends a bar I29 carrying a stud I33, on which a clutch-lever I34 is pivoted. By means of a roll !32, an upstanding arm I33 of said clutch-lever is articulated with the slidable clutch-element 56, the latter having a groove I34, Figure 13, embracing said roll. By means of a pair of cam-following arms I36 extending laterally from opposite sides of the clutch-lever pivot and toward the universal shaft IHI, as seen in Figure 15, said lever may be rocked for shifting the clutch-element 6B. Said universal shaft is accordingly provided with a pair of cams I38, I39 co-operating with said clutch-lever arms I36 to rock the clutch-lever. The cam I39 may be formed integrally with the aforementioned arm I I3 that rocks the totalizertruck-holding lever I I1.

When a digit is being registered in one denomination of the totalizer-trains, it may result at the same time that a number of trains of higher denomination are advanced one digitstep by the operation of the carry-over devices. In such case, the dial-wheels that are driven by the carry-over devices are likely to come to rest in spiral array, as indicated in Figure 13. This is due to the cumulative backlash of the several totalizer-gear trains and carry-over devices 86. The shift of the clutch-lever Hi to disconnect the master-wheel after the latter has been driven by the actuator-train to register a digit in the totalizer may be used to align the gears T5 for the purpose of correcting the spirality.

The clutch-element I3I is accordingly provided with an arm forming a gear-aligning blade having a straight beveled edge I43 of a length to engage, say, six of the totalizer-gears l5. Said gear-aligning edge i 3 is disposed above and laterally of the clutch-lever-pivot stud I30 so that in the master-whecl-disconnecting stroke of the clutch-lever I 3i, said edge I43 enters the spirally-arrayed totalizer-gears "I5 at a slant which progressively diminishes during said stroke of the clutch-lever. The totalizer-gears F5 are thereby aligned progressively from the lowest to the highest denomination engaged by said edge I43, as is indicated at Figure 15, which shows the clutch-lever partially operated to disconnect the master-wheel. Figure 2 indicates the aligning edge I43 fully engaged with the totalizergears I5.

For aligning the totallzer-gears 75 of the lower denominations not reached by the clutch-lever blade I42, an auxiliary blade I is provided and may also be operated by the full-stroke universal rock-shaft lei. Said auxiliary blade I45, in order to clear the clutch-lever blade M2, may enter the totalizer-gears 15 along a line that is one tooth-space behind the line along which the clutch-lever blade I42 operates, see Figure 14.

Mounted adjacent to the previously-described totalizer-truck-locking lever Ill, and swinging on the pivot-stud II8 of the latter, is a driving arm I4! for the auxiliary blade, reaching toward the universal-shaft arm IE3 and having a camslot I43 engaged by the roll II 4 of said latter arm. Said arm I41 thus driven by the universal shaft serves to move the auxiliary blade toward and from the totalizer-gears '15 in timed relation to the movement of the clutch-lever blade I42.

As seen in Figure 3, the auxiliary blade I45 is formed at the forward end of an arm I49, which, by means of perforated turned-down ears I53, I5I, is pivoted on a stud I52, threaded into the stud IIB, on which the driving arm I41 is pivoted. The ear l5I is extended downwardly for connection with a pin I projecting from the driving arm I41, said pin being articulated with a slot I54 at the lower end of said ear I5I. It will be seen that there is formed a lever which, for convenience of assembly, is separable into two parts, one part embodying the driving arm I 4?, and the other part embodying the described member on which the auxiliary blade I45 is formed.

The driving arm I4! is provided with a holding tooth I56 for engaging the master-wheel 63 to hold the latter against rotation while disconnected from the actuator-train pinion 58. The driving-arm-cam slot I48 has a dwell I5'I so that the initial portion of the universal-shaft movement which is effective to partly enter the clutchelement teeth 67 into the slotted flange 69 of pinion 58 (see Figure 10) is ineffective to move the driving arm Mt". It results therefore that the master-wheel-holding tooth I56 is not withdrawn from the master-wheel until the latter is coupled to the pinion 58. The positions of the parts at the instant when the master-wheel-holding tooth I56 is about to be withdrawn are indicated in Figures 8, 9 and 10.

Further movement of the actuator 43 from the Figure 8 position fully displaces the fullstroke pawl I03 to the position in which it trails along the actuator-edge I05, and consequently said further movement completes rotation of the universal shaft IOI, as indicated in Figure 11. While said universal-shaft rotation is being thus completed, the roll II4 of the universalshaft arm II3 sweeps over a camming portion I59 of the driving--arm-cam slot I48. The driving arm I4? is thereby swung to the Figure 11 position, in which the holding tooth I56 will have been withdrawn from the master-wheel. During said completion of the rotation of the universal shaft I I, the clutch-lever I 3I also becomes fully rocked to the position seen in Figure 10, thereby causing its gear-aligning blade I42 to be fully withdrawn; the clutch-element 66 will then also have been fully shifted leftward to the position seen in Figure 13. The driving arm I41 may be fully operated before the universal shaft IOI completes its rotation, and the cam-slot I48 of said driving arm may in such case be provided with a dwell-portion I60.

It will be seen, in Figure 11, that when rotation of the universal shaft I0! has been completed during a down stroke of the actuator, the totalizer-truck-locking lever II'I will also have been fully rocked. The movement of this lever H1 is also utilized to rock the appropriate carry-overdevice-supporting lever 89. There is accordingly formed at the top of the block II9 of said lever II! a master-dog I62, which, as set forth in the aforesaid Thieme application No. 468,175, engages a downward extension I63 of the carryover lever 89. These levers are engaged seriatim by the master-dog during the travel of the totalizer through a computing zone, for the purpose of raising that carry-over device 86 which couples the totalizer denominational train, engaged by the master-wheel, to the train of next lower denomination.

Further movement of the actuator downwardly from the Figure 11 position in concurrence with continuance of the stroke of the key-lever 25 will now rotate the totalizer-gear train whose gear '15 is over the master-wheel 63. It will be understood. that this latter ro ation is effected by means of the camming portion I26 of the actuator. To afford time for disconnecting the master-wheel from the actuator-train before the reverse movement of the actuator begins upon release of said key-lever, the rotation of the operated totalizer-train is completed before the completion of the down stroke of the actuator and key-lever. The camrning portion I26 therefore terminates in a dwell I65, which has the effect of holding the actuator-train-rock shaft 41 stationary during the final part of the actuator-stroke as effected by the down stroke of the numeral-key lever 25. It will be understood that as the actuator 43 and numeral-key lever 25 complete their down stroke, the corresponding type-bar 28 is caused to print against the platen 24. As soon as the upper end of the camming portion I26 of the actuator-cam slot reaches the roll II4, the point of the full-stroke pawl-finger I04 escapes from the upper corner I07 of the actuator-edge I05.

The spring I24 will thereupon rotate the unive sal shaft IOI reversely, and the clutch-lever fat, the driving arm I41 and the truck-locking lever i 57 will also be operated reversely in the timed relation established by the clutch-lever canis E26, i353, the driving-arm-cam slot I48, and the cam-slot of the totalizer-truck-locking lever ill Immediately upon such escape of the pawl the latter, under the influence of said spring I24, will be caused to swing upwardly far enough so that the tip of the pawl-finger I04 will be in the path of the upper corner I01 of the actuator before the latter reaches said pawlfinger in its return stroke. Figure 14 shows how the return stroke of the actuator may aid the reverse rocking of the universal shaft I0 I, the parts being shown in the position wherein, in furtherance of such aid, the pawl I03 has been rocked relatively to the universal shaft IOI against the force of the pawl-spring II2 until the inner end of the pawl-slot II 0 abuts the pin III. Figures 14 and 15 show how the auxiliary aligning blade I45 enters the gears I5 before the clutch-leveraligning blade I 42 enters said gears. It will be noted also in Figures 13 and 15 that the clutchlever I3I has been operated to partly shift the clutch-element 66 rightward. It will be further noted in Figure 14 that the upper dwell I65 of the actuator-cam slot is still traversing the roll 48. Thus, by the time the camming portion I26 of the actuator-cam slot (Figure 14) reaches said roll, the clutch-element will have been shifted to the right (from Figure 13) to fully disconnect the master-wheel, and the totalizer-truck-locking lever will have been returned to the Figure 4 position, with an accompanying restoration (of the carry-over device 86 and its lever 89 urged by spring I66) to the Figure 4 position. It will be further noted in Figure 14 that the masterwheel-holding tooth I56 on the driving arm I41 has been driven into engagement with the master-wheel 63 before the latter is fully disconnected from the actuator-train. The reverse movement of the driving arm I4'I to drive the master-wheel-holding tooth I56 and the auxiliary aligning blade into effective positions, is caused by the sweep of the roll I I4 over the camming portion I59 of the driving-arm-cam slot. After traversing said camming portion the roll moves idly, in respect to said driving arm, along the dwell I51.

In the continuation of the return stroke of the actuator 43 after the Figure 14 position has been reached, the full-stroke pawl will be caused to trail the edge I05 of the upwardly-moving actuator, as indicated at the actuator on the left in Figure '7. While so trailing said actuator, the inner end of the pawl-slot IIO abuts the pin III, and thereby holds the universal shaft IOI against counter-rotation from the normal position which said shaft has assumed under the pull of the spring I24 aided possibly by the upward thrust of the actuator against the pawl I03. This holding of the universal shaft has the effect of holding the pawl I03 shown at the right of Figure 7 against downward displacement, it being remembered that in the normal position of the universal shaft Ml, the pin iii abuts the outer end of the slot H0 of a pawl that is in neutral position. The actuator shown at the right of Figure 'l is representative of any actuator other than the actuator moving upward. It will be seen therefore that the looking or holding of the universal shaft It! by means of the trailing pawl of an upwardly-moving actuator has the effect of looking all the other actuators against operation until the trailing pawl escapes from the lower corner I56 of the upwardly-moving actuator. Said lower corner may be so arranged that the trailing pawl escapes therefrom just when the actuator reaches the end of its upward movement to come to rest against the face of the actuatorframe 3'1, as is indicated in Figure 6.

The normal position of the rock-shaft 4'! of the actuator-train may be established by means of an adjustable stop lE'i, Figure 6. A spring lfi i may be provided to urge said shaft 4'! to rotate until a pin E68 projecting from the shaft abuts said stop lfil.

Inasmuch as the carry-over devices 86 are operable reversely, it is not necessary to guard against reversal of the down stroke of the actuator during the time the camming portion 526 of the actuator-cam slot traverses the roll 48. For this reason, each actuator-edge m5 is provided with pawl-engaging notches Hi9 only at the upper and lower ends of said edge. Thus, as shown in Figure 7, two notches suffice at the lower end of the actuator-edge and one notch suffices at the upper end of said edge. The lower notches are so disposed that once the master-wheel is clutched to the actuator-train, by starting a down stroke of an actuator, said stroke must be completed. Similarly, the upper notch is so disposed as to prevent a repetition of a down stroke, before completing the return stroke, once the master-wheel has been disconnected from the actuator-train in said stroke.

The full-stroke pawls, operative as indicated in Figure '7 to prevent operation of more than one actuator, co-operate with the locking device embodied in the series of rods 553.

The operation of the mechanism is as follows: It may be assumed that the typewriter-carriage 23 has been tabulated to a position in which one of the totalizer-gears I5 is engaged with the master-wheel 63, as in Figure 13, for example. The numeral-key lever 25 is now depressed to cause the type-bar 28 to print against the platen 24 and at the same time enter the digit represented by said numeral-key lever into the totalizer 3i. In the first portion of the key-lever stroke, the actuator is swung to the Figure 8 position, and all the other key-levers have been locked by means of the rods 93 as soon as the link 43* of the actuated key-lever has entered between said rods 93. In Figure 8 the clutch-element 66 will have been shifted leftward to the position, seen also in Figure 10, to partly enter the slotted flange 69 of the actuator-train pinion 58. At this point, the carry-over device 86 has also been partly lifted, and the totaliZer-truck is partly locked by reason of the teeth I20 of the lever ill having entered the totalizer-truck rack I22. The partial shifts of the clutch-lever ISI, and of the totalizer-truck lever Il'l which also carries the master-dog IE2 for lifting the carry-over devices 86, have been caused by the displacement of the universal shaft till as seen in Figtu'e 8. This displacement of the universal shaft llli has been caused by the lower corner Hi6 of the descending actuator displacing the full-stroke pawl i533 downwardly. Further descent of the actuator 43, by reason of the continued stroke of the key-lever 25, brings the parts to the Figure 11 position, wherein the universal shaft I01 has reached the extreme of its swing since the fullstroke pawl now trails the actuator-edge [05. This completion of the swing of the universal shaft ilil will have shifted the clutch-element to the full extent of its leftward movement as seen in Figure 13, will also have caused the masterwheel-holding tooth N36 to have been fully withdrawn from the master-wheel, and will also have caused the aligning blades I42 and M5 to have been withdrawn from the totalizer-gears 15. It will be seen, in Figure 11, that the camming portion 26 of the actuator is about to traverse the roll 48 on the arm 48 of the rock-shaft 41 to cause the latter to rock and thereby draw down the gear-sector 52 to rotate the pinion 58. Rotation of said pinion 58, now connected to the master-wheel 63 by the clutch-element 66, will cause the denominational train of the totalizer with which the master-wheel is engaged to be rotated while said actuator-camming portion iZG traverses the roll 48. When the upper end of the actuator-camming portion I26 has reached the roll and the upper actuator-dwell portion 165 is about to engage said roll, the rock-shaft 41 will have been fully rocked, and the full-stroke pawl is now permitted to escape from the upper corner Nil of the actuator. During the escape of said pawl, the down stroke of the actuator continues and the type-bar 28 is caused to print against the platen 2 3. As soon as the full-stroke pawl I03 escapes from the upper actuator-corner Hl'l, the spring 526 of the universal shaft Ifil urges the latter to return to the normal position seen in Figure 4, thereby carrying all the full-stroke pawls back to their normal positions, the normal position of the universal shaft being indicated in Figure 4. In the return swing of the universal shaft from the Figure 11 position to the Figure 4 position, all the parts operated by said universal shaft, namely, the carry-over lever 89, the clutch-element 66 and its lever l3l, the trucklocking lever ill and the aligning-blade-driving arm Ml, which, it will be remembered, carries the master-wheel-holding tooth 156, are returned to their normal positions. The return of these parts to their normal positions will have been completed by the time the actuator in its return stroke is slightly past the Figure 14 position, or, in other words, when the camming portion I26 of the actuator is about to traverse the roll 48. At this point the rock-shaft M is about to be rotated reversely, and it will be understood that such reverse rotation can now have no effect on the totalizer, since the master-wheel 63 has been disconnected from the actuator-train by the completion of the rightward shift of the clutch-element G6 and is then held by the tooth I56. During the return stroke of the actuator, the fullstroke pawl I03 trails the actuator-edge reversely, as indicated in Figure 7, the universal shaft till during such reverse trailing of the pawl being in its normal position as indicated in Figure 7. In the normal position of the rockshaft and with one of the pawls Hi3 trailing a returning actuator, all the other actuators are held against contrary movement by means of their respective pawls Hi3 which abut the pins I i I of the universal shaft EEH. Not until the pawl of the returning actuator escapes from the lower corner I68 of said returning actuator can another actuator be operated on a down stroke. It will be evident that the lower corners I06 of the actuators may be so disposed that the escape of the full-stroke pawls therefrom cannot occur until the actuator is fully returned to the Figure 6 position. Hence, irrespective of the time interval at the end of the returning key-lever stroke when the locking rods 93 are likely to be ineffective on account of the emergence of the lip 94 of the link 43 from said rods, no other actuator may descend until the returning actuator is fully restored.

Variations may be resorted to within the scope of the invention, and portions of the improvements may be used without others.

Having thus described my invention, I claim:

1. In a computing machine having a row of denominational, totalizer-gears, and also having a master-wheel for engaging the totalizer-gears in denominational order, said master-wheel being normally disconnected from a set of differential actuators, there being provided a shiftable clutchelement, whereby, upon operation of an actuator, the master-wheel may be connected to the actuator, and subsequently disconnected again; in combination, an actuator-controlled pivoted lever for shifting said clutch-element, said lever having an arm forming a gear-aligning blade operative, upon said disconnection of the masterwheel, to engage the teeth of and thereby align the totalizer-gears, the blade being disposed relatively to the lever-pivot so as to have a tilting movement and to be thereby seated in the totalizer-gears progressively from lower to higher denominations, said blade being withdrawn from said teeth when said lever is operated to connect the master-wheel.

2. In a computing machine having a totalizer, totalizer-actuating mechanism including a master-wheel, and also including a series of individually reciprocable digit-entering actuators for driving said master-wheel, said master-wheel being normally disconnected from said actuators, the combination of means including a shiftable clutch-element for connecting the master-wheel to any operated actuator and subsequently disconnecting the same again at predetermined points of the actuator-stroke, a rock-shaft common to all the actuators, and rocked to and fro by every cycling of any one of the latter, said rock-shaft having a pair of complementary cams thereon and spaced lengthwise thereof, and an operating lever articulated to said clutch-element and having arms to abut and follow said cams, said lever being mounted to turn about an axis extending crosswise of said shaft, and being constantly controlled by said cams, said cams being timed to connect and disconnect the master-wheel at said points of the actuatorstroke.

3. In a computing machine having a totalizer, totalizer-actuating mechanism including a master-wheel, and also including a series of individually reciprocable digit-entering actuators for driving said master-wheel, said master-wheel being normally disconnected from said actuators, the combination of means including a clutch for connecting the master-wheel to any operated actuator and subsequently disconnecting the same again at predetermined points of the actuatorstroke, a rock-shaft common to all the actuators, and rockable by any one of the latter, and a clutch-operating lever operable by said rockshaft to connect and disconnect the master-wheel at said points of the actuator-stroke, said totaliz er having a denominational series of geartrains co-operative seriatim with the masterwheel, said clutch-lever having an arm extending transversely of the gear-trains and thereby forming a gear-train-aligning blade.

4. In a combined typewriting and computing machine having a totalizer and a master-wheel therefor, numeral type-keys, and a set of differential actuators reciprocable selectively by said keys, the combination of a cycling rock-shaft common to all the actuators, a series of followers for engaging the actuators, each follower swiveled upon said rock-shaft, said rock-shaft and said followers having co-operative stops limiting the swing of a follower relatively to said shaft, a spring for each follower constantly urging the latter against one of the stops, an abutment for said shaft, and a spring urging said shaft against said abutment, so that the followers are normally held poised between their actuator-trailing positions, said stops being arranged so that the shift of a follower to trail an actuator in a computing stroke rocks the shaft-member from said abutment, said follower escaping at the end of the computing stroke and returning to its normally poised position with the cycling shaft, the limited swing of the follower relatively to said shaft permitting it to be reversed for trailing the actuator in the return stroke, the reversal of the follower bringing the other stop into action to prevent rocking of said cycling shaft in the direction away from normal position against said abutment.

5. In a computing machine, the combination with a totalizer-operating master-wheel, a row of individually-reciprocable digit-entering actuators therefor, and a clutch for connecting said master-wheel to a common train differentially actuated by said actuators, of a clutch-operating rock-shaft, means co-acting with said actuators whereby said rock-shaft is caused to be rocked in opposite directions at the beginning and conclusion of a computing stroke of any actuator, an operating lever for said clutch, and complementary cams on said rock-shaft having constant control over corresponding arms provided on said clutch-lever to actuate said clutch-lever to connect and disconnect the master-wheel positively as said shaft is rocked.

6. In a combined typewriting and computing machine having a totalizer and a master-wheel therefor, numeral-type keys, and a set of differential actuators reciprocable selectively by said keys, said master-wheel being operable by said actuators individually but normally disconnected therefrom, the combination of a set of shiftable followers to co-operate individually with said actuators, each follower trailing its actuator oppositely during opposite strokes of the latter, and escaping therefrom at the end of each stroke, a cycling element universal to said followers, and means detaining said cycling element in normal position, each follower being displaceable by its actuator and effective to move said cycling element from normal position, each follower when operated by its associated actuator being effective to connect the actuator to the masterwheel by means of said cycling element and maintain the connection during the computing stroke of its key, and then release the connection, said follower escaping from the actuator at the end of the computing stroke and returning with said cycling element to normal position, means being provided whereby the escaped follower in its reverse shift by its returning actuator moves relatively to and thereby locks said cycling element in its resumed normal position throughout the return of the key.

7. In a combined typewriting and computing machine having a totalizer and a master-wheel therefor, numeral-type keys, and a set of differential actuators reciprocable selectively by said keys, said master-wheel being operable by said actuators individually but normally disconnected therefrom, the combination of a cycling rockshaft common to all the actuators, a series of followers for engaging the actuators, each follower swiveled upon said rock-shaft, said rockshaft and said followers having co-operative stops limiting the swing of a follower relatively to said shaft, a spring for each follower constantly urging the latter against one of the stops, an abutment for said shaft, and a spring urging said shaft against said abutment, so that the followers are normally held poised between their actuator-trailing positions.

8. In a computing machine having a row of denominational totalizer-gears, and also having a master-wheel for engaging the totalizer-gears in denominational order, said master-wheel being normally disconnected from a set of differential actuators, there being provided a shiftable clutch-element, whereby, upon operation of an actuator, the master-wheel may be connected to the actuator, and subsequently disconnected again; in combination, an actuator-controlled member for shifting said clutch-element, said member constructed with a gear-aligner operative, upon said disconnection of the masterwheel by means of said member, to engage the teeth of and thereby align the totalizer-gears, said gear-aligner being withdrawn from said teeth when said member is operated to connect the master-wheel, whereby said member serves both as a clutch-element shifter and a totalizergear aligner.

9. In a computing machine having a series of individually operable digit-entering totalizeractuators movable in computing and return strokes; a master-wheel, a rockable cycling element therefor common to all the actuators, a series of trailing followers for engaging the actuators, each follower transversely perforated and thereby independently journaled on said cycling element, said element and said followers having cooperative stops limiting the abnormal swing of a follower relatively to said element, a spring for each follower constantly urging the latter against one of the stops, an abutment for said rockable element, and a spring urging said element against said abutment, so that the followers are normally held poised between their actuator-trailing positions.

10. In a computing machine having a masterwheel, a driving-clutch mechanism therefor, and a series of individually operable digit-entering totalizer-actuators movable in computing and return strokes; a rockable cycling element common to all the actuators, and controlling said clutch-mechanism, a series of followers for engaging the actuators, each follower transversely perforated and thereby journaled for independent movement on said element, said element and said followers having co-operative stops limiting the swing of a follower relatively to said element, a spring for each follower constantly urging the latter against one of the stops, an abutment for said rockable element, and a spring urging said element against said abutment, so that the followers are normally held poised between their actuator-trailing positions.

11. In a computing machine of the character described, the combination with a reciprocatory computing-mechanism actuator, of a follower trailing said actuator in reverse directions during the opposite strokes of the latter, a cycling element serving as a fulcrum-member for said follower, mounted for rocking movement from and back to a normal stop position, said cycling element being constantly urged toward said normal position, said follower being pivoted on said cycling element so as to be capable of an independent limited abnormal swing thereon, whereby, in one direction of the actuator-movement, the shift of the follower to trailing position rocks said cycling element, and whereby the actuator gives the follower an abnormal swing relatively to said element as it is shifted to trail the actuator in the opposite direction, said cycling element being in its normal position during the latter shift of said follower, a master-wheel connecting and disconnecting train, and mechanism controlled by said cycling element for controlling said train.

12. In a computing machine having a totalizer, a totalizer-master wheel, individually reciprocatory digit-entering actuators operable in computing and return strokes, and a train operable by any actuator for driving said master-wheel, the combination of a cycling element, a clutch, clutch-operating means controlled by said cycling element whereby said master-wheel is connected and disconnected to and from said train at the beginning and end respectively of a computing stroke of any actuator, a plurality of followers, each individually shiftable, and means whereby the active follower is effective to operate said cycling element to actuate said clutch to connect and disconnect said master-wheel at the beginning and end of any computing stroke.

13. In a computing machine having reciprocatory digit-entering actuators individually operable for driving amaster-train which operates totalizer-elements in denominational order to compute, said master-train normally ineffective to operate the totalizer-elements, the combination of a cycling element, means for enabling it to render said master-train effective, a plurality of followers, one for each actuator, each follower being movable independently of the cycling element, said followers being individually shiftable by their respective actuators, at the beginning and end of the computing strokes of said actuators, and means whereby the individual shift of any follower at the beginning and end of the computing stroke of its actuator is operative to render the master-train effective prior to the forward rotation of the master-wheel and ineffective prior to the idle reverse rotation of the master-train.

14. In a computing machine having a row of individually reciprocable digit-entering actuators, a master-wheel, and a totalizer having a series of computing wheels, the combination of a cycling element having control cams, means directly engaged and positively controlled by said cams upon said cycling element to make and break a connection between the active actuator and said master-wheel, a series of followers, each movable while the other followers remain idle in normal position, said cycling element being operable by any of said actuators through its follower, means to restore said cycling element upon the escape of the active follower from its actuator at the conclusion of the computing stroke thereof, each follower being also movable independently, of the other followers, and said cycling element, to abnormal position by the return stroke of its actuator, to intercept said cycling element andprevent operation thereof by any other follower, and means to insure said cycling element having permanent control of said master-wheel, including a detent normally engaging said master-wheel and having a direct cam-connection to said cycling element, to steady said masterwheel during the operation of connecting it to the actuator, and to release the masterwheel as soon as so connected.

15. In a computing machine having a row of individually reciprocable digit-entering actuators, a master-wheel, and a totalizer having a series of computing wheels, the combination of a cycling element having control cams, means including a shiftable element directly engaged and positively controlled by said cams to effect a connection and disconnection between the active actuator and said master-wheel, a series of followers, said cycling element being operable by any of said actuators through its follower, means to restore said cycling element upon the escape of the active follower from its actuator at the conclusion of completing the stroke thereof, each follower being also movable to abnormal position by the return stroke of its actuator to intercept said cycling element and prevent operation thereof by any other follower, a detent normally engaging said master-wheel, an arm having said detent thereon and having a direct cam-connection to said cycling element, to maintain said master-wheel detented during the operation of connecting it to the actuator, and to release the master-wheel as soon as connected to the actuator, a primary aligner for a number of computing wheels adjacent said master-wheel, said aligner being provided upon said detent-arm, to align the computing wheels adjacent to the master-Wheel at the re-detenting thereof at the conclusion of the computing operation, and a supplemental aligner mounted upon said shiftable element of said master-wheel-disconnecting means to come into operation subsequently to the primary aligner, to complete the alignment of a number of wheels more remote from the masterwheel.

16. In a computing machine having a row of individually reciprocable digit-entering actuators, a master-wheel, and a totalizer having a series of computing wheels, the combination of a cycling element, a cam-device operatively engaged by said cycling element and having means for controlling a connection between the active actuator and said master-wheel, a detent normally engaging said master-wheel and having a direct cam-connection to said cycling element, to steady said master-wheel during the connecting operation and to release the master-Wheel when connected to the actuator, an aligner for a number of computing wheels, said aligner being mounted upon said detent to move as a unit therewith under control of said cam-connection to align the computing wheels adjacent to the masterwheel at the conclusion of the computing operation, and a final aligner mounted upon said connection-controlling means to operate under control .of said cam-device to come into operation subsequently to the first aligner to complete the alignment of a number of wheels more remote from the master-wheel.

17. In a computing machine having a row of individually reciprocable digit-entering actuators, a master-wheel, and a totalizer having a series of computing wheels, the combination of a cycling element operable by any actuator, a device operatively engaged by said cycling element and having means to control a connection between the active actuator and said master-wheel, a detent normally engaging said master-wheel, a cam associated with said cycling element to control said detent, said cam having a dwell to steady said master-wheel during its connection to the actuator, and having a part to release the master-wheel when so connected, and an aligner connected to said detent to move as a unit therewith under control of said cam to align a number of computing wheels at the conclusion of the computing operation.

18. The combination with a set of digit-key levers, a set of actuators operated thereby, a totalizer-operating master-wheel, and a normally disconnected train, to connect said actuators to said master-wheel, of a single cycling element operable by any of said actuators and in the form of a rock-shaft carrying a set of followers for trailing said actuators, each actuator formed with a trailing edge having lower and upper terminal shoulders, each follower being independently pivoted upon said rock-shaft to swing individually relatively thereto, and means for limiting the relative swing of each follower and for enabling each follower to rock the rock-shaft when the follower is depressed by said lower shoulder, while the remaining followers remain in normal positions and prevent re-operation of the cycling element, each actuator effective by means of its trailing edge to lock its follower and the cycling element in their operated positions.

19. In a computing machine having denominational totalizer-elements engageable seriatim with a master-wheel, the combination with a reciprocatory digit-entering actuator for said master-wheel, operable in computing and return strokes, of means including a clutch-element for positively connecting and disconnecting the actuator and master-wheel, at the beginning and end respectively of the computing stroke, a cycling element in the form of a cam-shaft rockable in opposite directions in timed relation to the beginning and end of the actuator-computing stroke, and a clutch-element lever operated by said cam-shaft, said cam-shaft having a pair of, spaced complementary cams, and said lever having opposite rigid arms following said cams and constantly controlled thereby.

20. The combination of a totalizer having computing wheels, a. normally disconnected masterwheel for operating them, a set of key-controlled differential reciprocatory actuators to operate the master-wheel, means, including a cycling shaft, for effecting connection and disconnection of the master-wheel from the totalizer, said cycling shaft having followers operable independently of one another and associated with the various actuators, each follower being depressible from normal position by its actuator and thereby caused to effect a movement of said shaft in one direction, until the follower escapes from the actuator trailing edge, and spring means for restoring to normal position the operated follower when it escapes from the actuator trailing edge and for returning the cycling shaft simultaneously to normal position, said actuator returning upon release of the key, said operated follower being lifted by the same trailing edge throughout the return of the actuator and thereby moved relatively to said cycling shaft to lock and prevent premature operation of said cycling shaft by any of the remaining followers, the cycling shaft being retained in normal position during the return of the active actuator.

21. In combination, groups of computing wheels corresponding to a multiplicity of denominations in a totalizer, and carry-over trains, a primary aligning blade timed to engage a group of computing wheels to align them and thereby cooperate with the carry-over gear-trains to improve the positions of a group of next-higherdenomination computing wheels, and a co-operative automatic swinging supplemental aligning blade having a wheel-aligning edge coextensive with said group of higher wheels and mounted to swing said edge between an oblique position of retraction and a non-oblique effective position relative to said higher wheels, whereby the primary blade may co-operate with the trains to fully correct the positions of the wheels in its own group and partly correct the positions of the remaining wheels, preparatory to the concluding correction of the latter in seriatum order by the second aligning blade.

22. The combination with a totalizer, a masterwheel therefor, a master-wheel-driving train, a set of reciprocatory actuators for operating said train difierentially, and means for effecting connection of said driving train to said master-wheel, of a cycling element, and a series of followers co-operative with said actuators, and operatively associated with said cycling element so that each follower is individually displaceable by its associated actuator to actuator-trailing position to operate said cycling element for making said connection, the active follower and the cycling element being self-returning to break said connection upon escape of the follower from its actuator at the end of its computing stroke, the escaped follower being moved, independently of said cycling element, to trail its actuator reversely during the return movement of the latter to normal position and thereby lock the cycling element in said normal position to lock all of the inactive followers in normal positions in the paths of their respective actuators, whereby another actuator cannot operate said cycling element to reconnect said driving train and said master-wheel in advance of the completion of the return stroke of the active actuator to normal position.

23. The combination with a totalizer, a masterwheel therefor, a master-wheel-driving train, a set of reciprocatory actuators for operating said train differentially, and means for effecting connection of said driving train to said master-wheel, of a cycling element, and a series of followers co-operative with said actuators, and associated with said cycling element to operate the latter to make and break said connection, and to pre vent reconnection of said driving train and said master-wheel in advance of the completion of the return stroke of the active actuator to normal position, said cycling element mounted for rocking movement and extending along the set of. master-wheel actuators, each follower being transversely perforated and thereby independently journaled on said cycling element, said element and said followers having cooperative stops limiting the swing of a follower relatively to said element, a spring for each follower constantly urging the latter against one of the stops, an abutment for said cycling element, and a spring urging said cycling element against said abutnient, so that the followers are normally held poised between their actuator-trailing positions.

24. In a computing machine having a totalizer, totalizer-actuating mechanism including a master-wheel, and also including a series of individually reciprocable digit-entering actuators operable in computing and return strokes for driving said master-wheel, the combination of a series of followers, each individually displaceable from a neutral position by a computing stroke of its actuator, a cycling element common to all the followers and rockable by each thereof incidentally to its displacement from neutral position for connecting said master-wheel and the active actuator, and a locking lever normally engaging and holding the master-wheel against rotation, said locking lever having a positive connection to said cycling element, to be operable by and under constant control of the latter for releasing the master-wheel after connection thereof to any actuator, and re-locking the masterwheel prior to its release from the actuator, each follower being displaceable reversely by its returning actuator and relatively to said cycling element to thereby lock the latter in neutral posi- 'tion and concomitantly lock said lever in looking position during said actuator-return.

25. The combination with a totalizer having computing gears and a master-wheel therefor, a gear-train, reciprocatory actuators for operating said gear-train differentialiy, and means for connecting said gear-train to said master-wheel, of a cycling element controlling said connecting means, a series of followers co-operative with said actuators, said cycling element being operative under control of said followers so as to move from a normal idle position at a computing stroke of any actuator, return to said normal position at the end of said computing stroke, and be locked in said normal position by the actuator during the return stroke of the latter, and an aligner-blade normally engaging said computing gears, said blade having, for its withdrawal from and restoration to normal position, a positive connection to said cycling element so as to positively follow the movements of the latter from and back to normal position, and be locked in computing gear-engaging position when the cycling element is locked during the return of any actuator.

26. The combination with a set of digit-key levers, a set of actuators operated thereby, a totalizer-operating master-wheel, and a normally disconnected train, to connect said actuators to said master-wheel, of a single cycling element operable by any of said actuators and in the form of a rock-shaft carrying a set of followers for trailing said actuators, each actuator formed with a trailing edge having lower and upper terminal shoulders, each follower being independently pivoted upon said rock-shaft to swing individually relatively thereto, means for limiting the relative swing of each follower and for enabling each follower to rock the rock-shaft when the follower is depressed by said lower shoulder, while the remaining followers remain in normal position and prevent re-operation of the cycling element, each actuator effective by means of its trailing edge to look. its follower and the cycling element in their operated positions, said follower escaping from said upper shoulder preparatory to return of said follower and cycling element, and means for limiting the return of said cycling element so that the follower by its reverse displacement by said upper shoulder moves relatively to and thereby locks said cycling element against re-operation by said remaining followers during the independent return of the active actuator to normal position.

27. The combination with a totalizer, a master-wheel therefor, a carriage for effecting relative travel of said totalizer and master-wheel, and key-operated actuators to drive said masterwheel, of a cycling rock-shaft rocked in one direction by any of said actuators at the beginning of the down stroke of a key and released by the actuator to rock in a return stroke at the conclusion of the down stroke of the key, a pivoted aligner blade spanning a number of com puting wheels of said totalizer and having an aligning edge normally in mesh with said wheels, and means for enabling said cycling rock-shaft when rocked in said first direction to swing said blade upon its pivot out of mesh with the wheels and with its aligning edge inclining away from the wheels as said blade is so swung, said cycling rock-shaft having a returning spring and also having a cam operating at the return stroke of said rock-shaft, at the last part of the key-depression, to swing said blade upon said pivot to align said computing wheels one after another, said blade being normally eiiective upon additional wheels as the carriage travels.

28. The combination with a totalizer, a masterwheel therefor, and actuators for the masterwheel individually operable in computing and return strokes, of a gear-train common to the actuators, a normally open clutch from the geartrain to the master-wheel, aprimary aligning blade normally engaging a plurality of totalizerwheels, a supplemental aligning blade normally engaging a plurality of other totalizer-wheels, a cycling element connected to be rocked to and fro at the start and end respectively of any actuator computing stroke, connections enabling said cycling element to close said clutch and withdraw said aligning blades preparatory to the rotation of the master-wheel in a computing stroke, and a detent normally engaging the master-wheel, and controlled by said connections for maintaining said master-wheel in a detented condition during the operation or" clutching the same to said gear-train, and for thereupon withdrawing the detent from the master-wheel preparatory to the rotation of the master-wheel, said connections effective to maintain said aligning blades in effective positions while the master-wheel is maintained in detented condition and to withdraw said aligning blades with the master-wheel detent, said connections being arranged to be effective in the return rocking of said cycling element to move said supplemental blade into engagement with its wheels after the operation of the primary aligning blade upon its plurality of wheels and to concomitantly return said detent to efiective position, said connections also being arranged to co-operate with said cycling element and any actuator to lock said aligning blades and detent in efiective positions during the return stroke of said actuator.

29. In a computing machine having a series of totalizer-gears, a master-wheel therefor, digitentering actuators individually reciprocable in computing and return strokes, and a master-train operable differentially by the several actuators for driving said master-wheel, said master-wheel being normally disconnected from said mastertrain; the combination of a clutch-element shiftable for effecting connection and disconnection of the master-train and master-Wheel, a connection and disconnection controlling rock-shaft common to all the actuators, devices effective, under the control of any actuator, to rock said shaft in opposite directions at the start and end portions of the actuator computing stroke, said rock-shaft having a pair of complementary cams thereon and spaced lengthwise thereof, and an operating lever articulated to said clutch-element and having arms to abut and follow said cams, said lever being mounted to turn about an axis extending crosswise of said shaft and being constantly controlled by said cams, said cams being timed to connect and disconnect the master-wheel positively by the rocking of said shaft in said opposite directions.

30. Machine constructed according to claim 29, having cycling means operative at every to and fro rocking motion of said shaft for generally serving to insure full down strokes and full up strokes of the actuators, and to detent and release the master-wheel, and to align the totalizer-gears, and also to prevent untimely operation of another actuator.

HENRY L. PITMAN. 

